Radial steam motor



July 15, 1952 Filed May 13, 1948 A. E. HALL I 2,603,194

RADIAL STEAM MOTOR 6 Sheets-Sheet 1 INvENToR, ALLEN E. HALL ATTORNLYS- July 15," 1952 Filed May 13, 1948 A. E. HALL 2,603,194

RADIAL STEAM MOTOR 6 Sheets-Sheet 2 INVEN ALLEN E.

ATTORNEYS.

July 15, 1952 A. HALL RADIAL STEAM MOTOR 6 Sheets-Sheet 4 Filed May 13, 1948 hwzm'om ALLEN E. HALL.

F: G. IO.

ATTORNEYS.

July 15, 1952 A. E. HALL RADIAL STEAM MOTOR Filed May 13, 1948 6 Sheets-Sheet 5 INVENTOR, ALLEN E. HALL ,n 6622/ ATTORNEYS.

6 Sheets-Sheet 6 Filed May 13, 1948 NVENT-OR) ALLEN E, HALL ATTORNEYS.

Patented July 15, 1952 UNITED STATES PATENT 'FFlCEjf-ii v 2,603,1El4 I v 11}? RADVIAL'STEAM Moron Allen E. Hall, Philadelphia, Pa. 7 Application May 13, 1948, SerialNo, 26,823

6 Claims. (C1. 1215-121) 1 This invention relates to a radial steam motor. An object of this invention is the production of a radial motor that is operated by fluid pressure and which is capable of a fast reverse and a short cut-off and continuous expansion with heavy loads.

Another object of the invention is the construction of a novel and efficient radial motor that has a double annular ring of cylinders and a plural number of crank shafts mounted on bearings and having at their outer ends pistons with-'- inthe cylinders and connected to cranks by rods and capable of producing a rotary motion.

A further object of the invention is the construction of a radial motor having a timing gear centrally located and having outwardly mounted crank shafts, with a crank on each end set at 180 degrees, with a pinion gear secured to the crank shaft and meshing with the timing gear, with all the cranks equally spaced and set at a different degree to produce a continuous piston power stroke. v

A still further object of the invention is the construction of'a radial motor that will produce a maximum amount of horse power as compared with the present-day motor.

With the foregoing and other objects in view. my invention comprises certain novel constructions, combinationsand arrangements of parts as will be hereinafter fully described, illustrated in the accompanying drawings, and more particularly pointed out in the appended claims.

In the drawings:

Figure 1 is a vertical transverse sectional view through the motor, showing particularly the cylinder and crank arrangement with the pressure valve located in the proper position for the operation of the motor.

Figure 2 is a vertical, sectional view of the gear case and the gear location for a slow speed motor drive.

Figure 3 is a longitudinal, vertical, sectional view. showing all working parts'of a fast piston speed and a slow drive shaft construction.

" Figure 4 is a fragmentary, sectional view showing particularly the piston cylinder and shaft construction. I

Figure 5 is a vertical, sectional view of the piston and connection rod of the motor.

a Figure 6 is a fragmentary, sectional view of the 2 pressure-admitting valve with hand reverse mechanism, while r v T Figure? is a vertical section through the valve ofFigure6. Figure 8 is a vertical, sectional viewof the power reverse motor used in place of the harid reverse for remote control. Figure 9 is a sectional view of the reverse motor capable of reversing the valve movement.

"Figure 10 is a fragmentary, sectional view of the high speed power shaft andbearings there'- for. V K

Figure 11 is a'se'ctional view showing amodified form of an inlet. pressure valve.v

Referring to the drawings (Fig. 1), the frame vl is made in two sections of the same design, so that when fastened together said sections produce'a double motor casing having a plural number of cylinders or liners l on'each side and a piston 2 in each cylinder l and a connecting rod3 connecting each piston 2, with 'a crank 4, and each crank 4 set at a diiferent angle equally divided for the purpose of making a staggered stroke, so no two pistons make a stroke at one time; the cylinders or liners ,l have, their inner ends threaded and screwed into the motor frame I, the outer ends pass through the motor, frame I and are each supported in a radial position with a packing l3 and a, gland M to prevent leaking'aroundthe outer end of the liner l This allows for expansion and contraction independent of the engine frame I and allows the cylinder I to expand lengthwise and also in diameter, and always remain round and fit the pistons and be the means of very close fits and free, movement of the piston 2, which-piston has several piston-rings 88 to make a pressure tight chamber 89. we 5 The motor pressure inlet valve 5 is a hollow, fiatdisc 5 having six ports to serve seven cylinders and the motor will make forty-two power strokeseach time the valve 5 makes one revolution'as the six ports in the valve pass theseven ports in the cylinders l and develop the fortytwo strokes of the pistons 2. This motor is' very reversible as the valve 5 now stands-the "cylinder port 8 on the lowerileft-hand side is register}.- ing with port I of the valve 5 and the crank! is inproper positionto move left, if pressure was applied in valve 5; this valve is drlvenby shaft 6, having two pins vv9 projecting into two annular slots I0, and the bottom of the valve is being turned to the left by pins 9. Now to reverse the valve movement, the valve 5 is moved to the left by a hand wheel GI and drive pins 9, allowing the valve to be turned equal to the length of the annular slot I0, and the valve 5 will be stopped by the drive pin 9 reaching the other end of the slot I0 and the port I in the valve will be registering with the port 8 of right cylinder and port I and 8 will be closed with cylinder on the left and opening the port I of the valve and port 8 of the cylinder on right; when the pressure is applied to valve 5, the crank 4 is in position to move to the right and cause the reverse in all the cylinders and always two cylinders will be in proper position to make the reverse on the front or back of the motor, and the main drive shaft 20 will rotate in the same direction; the hand wheel 6I is turned to reverse the motor.

The cylinder exhaust ports 35 are uncovered by the piston 2 and exhaust takes place while crank 4 passes the bottom of the stroke and but little compression can take place on the return stroke. As described hereinafter, the exhaust chamber is formed by the motor frame I extending around the cylinders and has heavy ribs II and forms a very large annular exhaust chamber 36 all around the cylinders I. The motor has suitable lugs I5 cast or bolted on thesides of the motor so that it can be fastened on asuitable foundation.

Referring to Fig. 2, which shows the gear arrangement and different shafts that form the motor, the large gear I8 is the timing gear and this meshed with the odd number of smaller gears I1. that operate the crank shafts and in order to develop a motorso no two power strokes take place at the same time, there is an odd number of crank shafts I8; the motor-may. have a large number of these crank shafts but always an odd number. The motor makes as many as 500 or more power strokes at one revolution of the timing-gear and no two strokes will take place at the same time and this gear arrangement havingfthe pinions meshed with timing gear is the means of developing a motor oper-. ated by crank shafts and pistons that will have a staggeredstroke and a continuous expansion and when using seven crank shafts I8,- the timing gear I6 will be si'x times larger than the pinion gears I! for the-purpose of staggering the stroke and make possible the. development of this high speed motor operating at a slow speed on the drive shaft 20 driven by thegearwheel Iii; this is meshed with the timing-gear I6 by two pinions I! for slow speed of three and one-half to one or slower and for high speeds, the gear I5 will be meshed direct with the timing-gear as shown in Fig. i0, and the motor may have a drive shaft speed of 2,000 revolutions or more, if desired, and by this gear arrangement this motor can operate at any desired pistonspeed and have any desired speed of the drive shaft, depending on the diameter ofthe drive gear I5 by the use of the tw'opin'ions I -I to drive the gear I 9; this doubles the force of the drive and gives this drive gear a, force equal to the two pinion gears and makes a very desirable means of great strength for the drive gear I9, when carrying heavy loads at slow speeds and when operating at high speeds with gear directly meshed with the timing-gear, the speed will be high and the load lighter; by the useofthis gear arrangement most, any speed can be developed on thedrive shaft 20 with the use" of any outside transmusion gears. This gear arrangement is inclosed by an oil tight case I I that has extended pockets for the pinions so the diameter of the case can be made smaller and the size of the motor reduced the gear case I I forms the ends and sides of the motor and this case II is made of two castings of same design fastened together by bolts or other means.

Referring to Fig. 3, the crank shaft I8 has a crank 4 mounted on each end set at 180 to make possible an evenly divided stroke within the many cylinders I as no two strokes can take place at the same time. This motor has a steady expansion by this crank and cylinder construction; the crank shaft I8 has a pinion gear I! centrally located and meshed with the timing-gear I6; the motor has a plural number of crank shafts and an odd number of cylinders on each side of the motor; each crank 4 is set at a different degree, equally divided to produce a steady expansion within the many cylinders and at a reasonable piston speed, this motor is capable of making 21,000 expansions per minute or 25 expansions per second in each cylinder I.

A gland I4 and a packing I3 allow the outer end of the liner I to expand free of the motor frame I and the liner I also is free to expand in diameter and will at all times remain round and fit the piston 2 and the motor cannotbe harmed by fast starting due to expansion:

The crank shafts I8 are made in two sections so they can easily be removed and the solid cyle inder bearings 22 replaced without disturbing the gears I! in the gear case 23. The crank shafts I8 are removed through hand hole by removing plate 49 and cylinder liners I are removed through hand hole by removing cover I2, and the pistons and connecting rods are removed through hand hol I2. The crank shafts I8 are a press fit into gear I1 and keyed or splined into hub and held together by a through bolt 2I. This construction makes possible removal of moving parts of the motor so they may be replaced without dismantling the whole motor.

The revolving pressure valve 5 can be replaced by the removal of the pressure chest casting 48 and sliding valve 5 out; this valve has a hub on the outer end 46 and a metallic packing the pressure within chest holds valve 5 on seat 48;

. shaft 20.

the area of the hub 46. must be greater than the port area of the valve 5. This is a balanced valve, with a light pressure holding it on its seat 48. The valve 5 is driven by the timing-gear shaft 6. by projecting pins 9 resting in annular slots ID in the hub of the valve 5. This valve 5' has a projecting stem 33 projecting into shaft 6, to line valve up to the seat 48. The timing-gear I6 is pressed on shaft 6, and also held in place by keys 2I. The shaft 6 is supported by bushing bearings 50, and oil rings 5| are used to prevent leakage of oil. The outer end of pressurechest 43 has a hand hole plate 44 to replace, or inspect the metallic packing 45 for leaks. The annular exhaust chamber 36 has exhaust outlets 32 with inlet pipes 38 to cylinders with exhaust ports 35 uncovered by the pistons at the bottom of the strokes; and two large annular exhaust chambers 36 extend around the cylinders I and provide a very free exhaust means, and the auxiliary exhaust port 31 in valve 5 prevents any back pressure on return stroke of pistons 2. The motor has two oil pumps 24, of the plunger type. operated by cams 25 onflmain' slow-speed. drive These pumps '24 will'operate in the reverse and deliver any desired pressure to the pressure.

oil donduitsrmade by-circular-channel bars 26 welded to the'moto'r frame 1 inside of the crank shaft bearings and permits forced feed lubrication to all parts of motor without oil pipes by drilling of the shafting. The main drive gear l9-is press fit on main drive shaft 20 and locked by keys 30. The drive shaft 20 is supported by two inner bushing bearings 39 and, two outer bearings 40. The shaft 20 will support a heavy load each end without-outboard bearings and make a desirable slow speed drive for heavy loads having the reduction gears .built within the motor construction. 7 The speedreduction is within the motor for any desiredspeed and no outside transmissionis required, for slow speed heavy-pulling.

In Fig. 4 is shown :crank .4. and cylinder liner I' and frame I. The gcylinder' liner I has its inner endthreaded and screwed into frame I and passes through the frame I atits outer end and has a packing gland l4 andga zpacklng [3 to allow the liner I to expand independent of the motor frame. The piston p2 and the, liner. l can expand equally in all directions-and also be a means suitable for a close fit and prevent motor from damage by unequal expansion. The cylinder I? is surrounded by a large exhaust chamber 38 and ports 35 uncovered by piston 2 allows the exhaust into chamber 36 atthe b ttm of the.

stroke and the ports: are closed by the upward movement of piston and all pressure in the cylinder l is relieved by port 31 in valve 5 on the upward stroke of the, piston and in casepany water is pocketed within the cylinder I, the check valve 52, having a stiff spring 53, is capable of holding valve52 on the seat under normal loads and release the excess pressure in caseof backing up water in the cylinder. A Theexcess heat of the cylinder I is insulated from the gear case 23 by a jacket of cooling liquid 21 and also a jacket of heat insulating material 28 inside of exhaust chamber. .The lubricating oil is carried through a conduit26 welded to the motor frame and carrying the oil to all moving parts by drilled holes. The connecting rod bearings 52' and piston pi n 53'jhave an oil cooling system by forced feed lubrication. The connecting rod 3 has bushing bearings and is made in two sections and screwed together and locked by a through bolt 54 thatlocks rod in the proper position. The crank is hollowed out to form an oil cavity 55 and has a cover plate 56. Connecting rods 3 are provided with centrally positioned hexagonal sections to facilitate the use of a wrench in tightening the rods.

1 In Fig. 5, the piston 2 with a new type connecting rod that has no cap bolted at the bottom end and can be made shorter than the present design and has. replaceable bronze bushing 52' that requires no adjustment, and can be easily replaced, and the end plate 56 can be removed and a thin feeler used to find'out if bushing needs to be replacedwithout any parts of the rod being removed, and if the bearing 52 does need replacing, a new bushing can be quickly replaced without any fitting and be tested without turning over the motor by revolving the lower end of connecting rod on the crank bearings before screwing the two parts together.

The trunk piston has a pressure relief valve 52 mounted in the end to relieve any back pressure over the desired working pressure, and prevent damage to the motor.

The piston. pin '53 has heavy support ribs to relieve the piston Zofthe heavy load due to high The revolving hollow disc inlet valve 5 (Fig. ,6) has a stem 33 that supports the weight of the valve and holds it in line with theground seat. The stem projects within the end of the timinggear shaft '6 and revolves with this shaft and turns the timing-gear by two drive pins 9 that project in the hub of the valve 5 and rest within two annular slots I0 thatpermit the valve 5 to be moved ahead to reverse the motor. The valve 5 has aflat disc cut-off valve 59 mounted on the outer side of valve 5. The object of valve 59 is to open and close the inlet valve 5,,when reversing the motor. The valve 59 has gear teeth 60 cut around the outer edge and a hand wheel; 6| mounted on a shaft 62, and a gear 6 3 on the inner end meshed with gear 60 andby mflving the hand wheel 6!, the ports 31 or maybe opened and closed by the flat disc valve 5 9 being moved by said hand wheel 6l.- The flat valve 59 has two drive bolts 61 that operate in two annular slots 68. The slots are of the properlength to allow the fiat valve 59 to be moved so that ports 65 will register with the ports 31, or the ports 64, for the purpose of relieving the back pressure in the cylinders I after the exhaust ports have closed and piston moves up on return stroke these ports 31 or 64 are opened to relieve the back pressure; one set of ports 64 are open always, depending on the rotation of the motor; there are six ports 31 and six ports 64. The fiat valve 59 is moved in the proper direction by the hand wheel 61; this first moves the flat valve 59to open ports 31 and close ports 64, and also moves the intake valve 5, to the reverse position, and the drive'pinsfl stop the valve in the proper position by the length of the annular slots II]. This valve movement opcrates with the same efficiency, regardless of direction motor may be running, ahead or in the reverse, and about one-half turn of the hand wheel 5| reverses both valves 5 and 59 to the proper position. The hand wheel is held by a bracket 69, and coil spring 10 moves hand wheel inward and disengages gear 63 from teeth 60 on valve. 59 and no reverse ports are in operation when the motor is running.

The valve 59 is mounted on the hub of gear 5 with a revolving fit, and the flat disc spring 1! restingv on ball thrust bearing 12 holds the valveon seat 13, and the pressure of spring 1| also assist to'hold valve 5 on seat 48. The valve 59 revolves with valve 5. The valve 5 has suitable drilled holes for force-feed oiling. The hollow valve stem 33 is drilled for oil-cooling. The metallic packing 45 can be inspected by removal of hand hole plate 44. The pipe 14 is the pressure chest drain pipe.

The pressure valve 5 (Fig. 7) has ribs 15. These ribs 15 prevent valve 5 from being warped by the heat. The dotted port holes 55 show the position of the port holes of the seven cylinders, and the six ports 1 are in the valve 5 and show the admission port holes, and as port 1 registers with port 65, pressure is admitted to each cylinder and by having one less port in the valve 5 than the number of cylinders, no two power strokes can take place at the same time, and at the top of the valve is shown the cylinder port 65, and the valve inlet port 1 is registered and the piston 2 is in the position at the top of the stroke to re? ceive a pressure charge, but just before the piston reaches the top of the stroke, the pressure relief port 31 passes over cylinder port 65 and relieves the pressure in cylinder I through port 66 inflat valve59, shown atv bottom of Fig. 6. Theport 31 istim'cd to close before piston .2 reaches the top center-to form a compression in the clearance space just before the inlet .valve.1. opens the port; 55 and at the topof Fig. '7, the top of the valve I is turning' to the right. and the port 31 has passed the port 55 and. relieved the back pressure and inlet port 1 has registered with port 65 and the piston is properly timed to make a working stroke and as all ports 16 3 are closed'when thetopcf valve 5 is'moving to the right and can pass over port 85 without the loss of'pressure and piston passes to bott of stroke and exhaust through port holes at the bottom of the stroke uncovered by the piston and the cycle of one cylinder is finished. When the valve has moved so'that the first. .port 3.1 on the right has passed 65 and relieved compression, and the inlet valve port 1'has passedthe cylinder port 65, expansion takes place while the closed relief port 54 passes over inlet port 05 and the piston exhaust through the cylinder port holes 35 and the working'stroke is finished.

= looking atthe intake valve 5, the first cylinder port 65 on the left, the port 31 has j-ustreg istered with the cylinder port 65 and relieved compression and next the pressure valve port 1 will pass over 85 and charge thcylinder if and then the closed relief valve 66 will pass over during the expansion and no pressure willbe lost, and then the piston 2 will open ports 35 and exhaust will take place and the same operation takes place in all seven cylinders and no two cylinders can operate at the same time, and by moving intake, valve ahead by the hand wheel 6 i, the reverse of the engine takes place: Thefiat valve 59 moves first and opens ports 65 and closes ports 31- andthe pressure valve moves forward and causes the ports 1 to register with the port 35 of a cylinder onpa reverse stroke and the motor will reverse about thirty timesfa, minute by test of working model and model, cannot stall on ceng ters and has never failed to start or reverse, after many thousand trials and will start with aruil load at a slow speed and requires no flywheel. In Figures 8 and 9 is shownla power reverse for the radial steam motor. The fiat valve fishes gear teeth cut around the outer edge of the valve and a gear wheel 63 mounted on the inner end of shaft 62, mountedjon ball bearings 75, securely mounted in a casing 16. The shaft 62 has a fan" with radial blades and capable of operating in both directions and turning gear wheel 6.3...which is meshedwith teeth 60. in fiat valve 59 and by admitting pressure to inlet openinglS filling. chamber 19 and forcingpressure of a fluid through the inclined nozzles '89, causes. the fan wheel 11 to turn from right to left, turning the shafts! and revolving gear wheel 63 andby gear teeth 60 turn valve 5.9 and. reversing the motor in the same way as with hand wheel: 6 11. By the use of this pressure motor reverse several engines canbe operated. by remote control byoneoperator from the pilot house. (not shown) of. a ship, and to reverse the motor 16' fluid pressure is mitted at inletopening 8i, filling the chamber 82 and by passing through incline nozzles 83 against fan blades 11 will operate the fan wheel from left to. right and through shaft 62 and gear 63- and gear teeth 6 cause valve 59 tomoveand reverse the valve movement of the motor, and when using steam as the reverse fluid, the steam line may be drained of all water and: moisture through-the reverse motor16 by opening the go-ahead inlet opening. or the reverseopenings 18 and a1; and

. 8' the water, moisture and steam will pass through the fan blades 11 and pass out the exhaust-open:-

ins. Mi to themotor. exhaust m r ra by the use of this. reverse motor- 18, the main steam line can be drained of all water by remotecontrol before starting the propelling motor. The reverse motor 1.6 is a part of the. valve movement that makes possible the operation of marine engines from the pilot house. This reverse motor 16 is percent dependable, with no working parts of delicate construction, and'far more desirable thanflan. electric motor that maybe used by those desiring to operate -the.valve'movement. The starting motor is bolted to the. pressur'e'chest casing 43 .by bolts. andthe gearfil will-always remain meshed with the valve 59. The reverse motor 16 has ball bearings 15 that require little power :to operate the Ian 11 as this will operate in a vacuum on all condensing engines. The purpose of the reverse motor 16 is to reverse the valve movement and drain the steam line' of water. It has no part in starting the motor, as the valvemovement will'reverse and start the motor with full load. 1 I l InFig. 10, the high speed drive is shown, having the drive gear l9 meshed direct with the timing-gear I6. The drive gear I9 is a press-fit on shaft 20, and locked-by keys 30. The drive shaft has two long inner bushing bearings 39 and two outer roller bearings 40, capable of carrying a heavy load at high speed without outboard bearings, and for extremely'high speed the gear It! can be-cut on the drive shaft 20 and speeds upward of 2,000 revolutions will be possible with slow gear speeds, and the space and weight of the motor will be greatly reduced. Thegear oil pumps 58 will be mounted withinthe'crank case and driven direct from the drive shaft 20. and pump oil into a welded conduit 26 to all parts of the motor and as this motor has no split bear-' ings, theball and roller bearings'can be used on allbearings of this motor without change, in design. i 5 A sectional view of similar pressure valve is shown in Fig. 11, with a tapered seat. This valve may have greater area of ports and the larger ports may be more desirable for high speed and this valve has many good points, but the manufacture of the taper seat is more difficult and the upkeep not. so good as the valve with the flat seat, but in cases where its merits require it, this valve will be used in place of a ilat seat valve. The design is similar to the flat valve and its merits covered by the flatvalve descriptiomand for engines built, that do not reverse, the reverse fiat valve 59 vwill not be needed, and with the flat valve 59 removed one set of port holes in the pressure valve 31 (or in the valve 5) will always remain open. The second set of ports 64 will be needed only on reversible motors.

7 While I have described the preferred embodiments of my invention and illustrated the same in the accompanying drawings, certain minor changes or alterations may appear to one skilled in the art to which this invention relates during the extensive manufacture of the same, and I, therefore, reserve the right to make such changes or alterations as shall fairly fall withm the scope of the appendedclaims.

What I claim is:

1. In a radial steam motor, a. casing having sidewalls and a peripheral wall, a pair of spaced partitions each spaced from a respective side wall, bearings each disposed centrally of a re v9 spective partition; an *annular wall extending from each partition around the outer end of a respective bearing, a shaft'fjournalled in said bearings, hollow disk valve' carried byjrespective ends of said shaft andf 'bearing against the Iouter ends of the annular'walls with their pevalves having series of circumferentially spaced ports opening through the face bearing on the respective annular walL and rotating means'for said shaft. i

2. In a radial steam motor, acasing having side walls and a peripheral wall, a pair of spaced partitions each spacedv from a respectiveuside wall, bearings eachfldisposed centrally of a respective partition, an annular wall extending from each partition around the outer end of a respective bearing, a shaft journalled in said bearings, hollow disk valves carried by respective ends of said shaft and bearing against the outer ends of the annular walls with their peripheries projecting beyond said annular walls, supply means to supply steam to respective valves, said supply means including a nipple on each side wall alined with said shaft, a nipple on each valve fitting in the last named nipple, and steam chests carried by the side walls and fitting over the nipples, sets of cylinders having their axes extending radially of the axis of said shaft, each annular wall forming the base for a res ective set of cylinders, each of said cylinders having an intake port opening through the outer end of the respective annular wall, each of said valves having a series of circumferentially spaced ports opening through the face bearing on the respective annular wall, said rotating means for said shaft.

3. In a radial steam motor, a casing having side walls and a peripheral wall, a pair o spaced partitions each spaced from a respective side wall, bearings each disposed centrally of a respective partition, an annular wall extending from each partition around the outer end of a respective bearing, a shaft journalled in said bearings, hollow disk valves carried by respective ends of said shaft and bearing against the outer ends of the annular walls with their peripheries projecting beyond said annular walls, supply means to supply steam to respective valves, said sup ly means including a nipple on each side wall alined with said shaft, a nipple on each valve fitting in the last named nipple, and steam chests carried by the side walls and fitting over the nipples, sets of cylinders having their axes extending radially of the axis of said shaft, each annular wall forming the base for a respective set of cylinders, each of said cylinders having an intake port opening through the outer end of the respective annular wall, each of said valves having a series of circumferentially spaced ports opening through the face bearing on the respective annular wall, said rotating means for said shaft, each set of said cylinders being of unequal number and the respective valves each having one more port than the number of the cylinders in their respective sets.

4. In a radial steam motor, a casing having side walls and a peripheral wall, a pair of spaced l partitions each spaced from a respective side wall, bearings each disposed centrally of a respective partition, an annular wall extending from each partition around the outer end of a respec tive bearing-a shaft journalled in said bearings, hollow disk valves-.carriedby respective, ends of said shaftzand bearing against the outer ends of the annular. :wallswith their peripheries projecting beyond said annular walls, supply means to supply steam to respective valves, sets of cylindershaving their axes extending radially of the axis of said shaft, each annular wall forming the base for a respective set of cylinders; each of said cylinders having an intake port opening through the outerend of 'the respective annular walL-each of said valves having series of circumferentially spaced portsiopening throughtheface bearing, on therespective annular wall; and r0- tating means for said. shaft, bearings carried by the said partitions adjacent the;said peripheral Wall, said last bearings havingtheir axes in planes radial to' the axis of said shaft and extending in the planes of the axes of said cylinders, shafts in said last bearings having 'bellcranks on their 'ends; means connected to said bell cranks for driving the same from said ;cylinders and timing gears connecting said bell crank carrying shafts with the first shaft.

5. In a radial steam motor, a casing having side walls and a peripheral wall, a pair of spaced partitions each spaced from a respective side wall, bearings each disposed centrally of a respective partition, an annular wall extending from each partition around the outer end of a respective bearing, a shaft journalled in said bearings, hollow disk valves carried by respective ends of said shaft and bearing against the outer ends of the annular walls with their peripheries projecting beyond said annular walls, supply means to supply steam to respective valves, said supply means including a nipple on each side wall alined with said shaft, a nipple on each valve fitting in the last named nipple, and steam chest carried by the side walls and fitting over the nipples, sets of cylinders having their axes extending radially of the axis of said shaft, each annular wall forming the base for a respective set of cylinders, each of said cylinders having an intake port opening through the outer end of the respective annular wall, each of said valves having a series of circumferentially spaced ports opening through the face bearing on the respective annular wall, said rotating means for said shaft, each set of said cylinders being of unequal number and the respective valveseach having one more port than the number of the cylinders in their respective sets, bearings carried by the said partitions adjacent the said peripheral wall, said last bearings having their axes in planes radial to the axis of said shaft and extending in the planes of the axes of said cylinders, shafts in said last bearings having bell cranks on their ends, means connected to said bell cranks for driving the same from said cylinders, and timing gears connecting said bell crank carrying shafts with the first shaft.

6. In a radial steam motor, a casing having side walls and a peripheral wall, a pair of spaced partitions each spaced from a respective side wall, bearings each disposed centrally of a respective partition, an annular wall extending from each partition around the outer end of a respective bearing, a shaft journalled in said bearings, hollow disk valves carried by respective ends of said Shaft and bearing against the outer ends of the annular walls with their peripheries projecting --beyond said annular walls, supply means to supply steam to respective valves, sets of cylinders having their axes extending radially of the axis of said shaft, each annular wall forming the base for a respective set of cylinders, each of said cylinders having an intake port opening through the outer end of the respective annular'wall, each last bearings having their axes in planes radial to the axis of said shaft. and extending in the planes of the axes of said cylinders, shafts in said last bearings having bell cranks on their ends, means connected to saidbell cranks for driving the same from said cylinders, timing gears connecting said bell crank carrying shafts 'withthe first shaft, and exhaust means for said cylinders.

asreaencas crrnn The following references are of record in the tile 0! this patent:

Number N umber 12 UNITED STATES PATENTS- Name Date Hatfield r May 26, 1885 Benham Sept. 22, 1891 Weaver Dec. 20, 1892 Bruce Feb. 21, 1893 Wright June 25, 1895 Cole et al Mar. 31, 1903 Lufkin June 20, 1905 Morgan Aug. 17, 1915 Halsey Aug. 20, 1918 Murphy Jan. 10, 1922 Augustine Jan. 16, 1923 Freund Sept. 20,1932 Tankersley Aug. 21, 1934 Moore Nov. 19', 1935 Morton Mar. 4,1947 Sejarto Feb. 10, 1948 FOREIGN PATENTS Country Date Great Britain Dec. 14, 1906 

